Means for controlling hoists and winches



Oct. 27, 1953 J C SLONNEGER 2,657,011

MEANS FOR CONTROLLING HOISTS AND WINCHES Filed April 1, 1950 5Sheets-Sheet 1 John C. S/onneger INVENTOR. 30

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Oct. 27, 1953 J. c. SLONNEGER 2,657,011

MEANS FOR CONTROLLING HOISTS AND WINCHES Filed April 1, 1950 5Sheets-$heet 2 Jr r W R a: n J n m mm my 5. \8 C 3 n h 0 6 J m 3 0 9 6 84 5 5 5 3 2 & 9 5 J@ 6 4 o IIII uV IIII i. l 5 5 I I lllllllllll In 7 5O 8 0 5 5 4 4 5 4 3 l= 3 v 4 5 5 MW IF; I [g C 4 Oct. 27, 1953 J. c.SLONNEGER MEANS FOR CONTROLLING HOISTS AND WINCHES 5 Sheets-Sheet 4Filed April 1, 1950 John C S/onneger INVENTOR.

Patented Oct. 27, 1953 MEANS FOR CONTROLLING HOISTS AND WINCHES John C.Slonneger, Dallas, Tex., assignor to The Continental Supply Company,Dallas, Tex., a corporation of Delaware Application April 1, 1950,Serial No. 153,319

23 Claims. (Cl. 254-473) This invention relates to new and usefulimprovements in means for controlling hoists and winches.

The invention is particularly concerned with apparatus for controllingthe rotation of the cable reels of well drilling rigs, and in provisionfor maintaining a constant rate of feed and a constant drilling loadupon the drilling bit of such a rig.

One object of the invention is to provide a device of the characterdescribed includin a small motor which may be driven at variousascertainable speeds and which will regulate the paying-out of cablefrom a reel in accordance with such speed.

Yet another object of the invention is to provide a device of thecharacter described which may be set to maintain a given drilling loadupon a drill bit, and will maintain such load by regulating thepaying-out from the cable drum of a drilling rig the cable whichsupports the drill bit and drill stem assembly.

A particular object of the invention is to provide an improved device ofthe character described having a novel anchor for the dead end of thesupporting cable, in which compensation may be made for the size ordiameter of the cable, and which aids in the accuracy of controleffected by the entire apparatus.

A further object of the invention is to provide an improved device ofthe character described which is light and inexpensive in structure, butwhich adequately controls the heavy loads involved.

A still further object of the invention is to provide an improved deviceof the character described which properly controls a hoist or winch, butwhich allows manual or other types of control to be taken overimmediately.

A construction designed to carry out the invention will be hereinafterdescribed together with other features of the invention.

The invention will be more readily understood from a readin of thefollowing specification and by reference to the accompanying drawings,wherein examples of theinvention are shown, and wherein:

Fig. l is a side elevational view showing schematically a drilling rigassembly having incorporated therein a control apparatus constructed inaccordance with this invention,

Fig. 2 is an enlarged view of the cable reel controlling portion of theapparatus,

Fig. 3 is a schematic view of the assembly for controlling the flow ofdriving fluid to the control motor,

Fig. 4 is a view of a modified form of the brake lever couplinarrangement,

Fig. 5 is an enlarged view in elevation of a modified form of thedriving fluid control mechanism,

Fig. 6 is a view of a modified form of the deadline anchor,

Fig. 7 is a view, partly in elevation and partly in section, of amodified form of the control motor driving connection,

Fig. 8 is a vertical, sectional view of a further modification of thedriving arrangement shown in Fig. 7 and illustrating the clutchoperating mechanism,

Fig. 9 is an enlarged sectional View of the hydraulic cylinder andpiston coupling the control mechanism to the cable drum brake,

Fig. 10 is a vertical, sectional view taken upon the line Ill-Ill ofFig. 6,

Fig. 11 is a vertical, sectional view taken upon the line ll-l I of Fig.6,

Fig. 12 is a plan view, partly broken away, of the dead line anchor, and

Fig. 13 is an enlarged, fragmentary, plan view of the drivingarrangement shown in Fig. 8, illustrating the clutch actuatingmechanism.

In the drawings, the numeral [0 designates in general a drilling rig ofthe type generally employed for the drilling of wells, such as oilwells. The rig is shown in a very simplified. and schematic manner forthe purposes of illustration and for explanation of the mode ofapplication or this invention.

The rig includes the usual upright derrick it having a crown block l2 atthe upper end thereof, and a travelling block [3' suspended from thecrown block by a plurality of strands of cable H, in the usual manner.One end of the cable I4 is secured to an anchor I 5, and the other endof the cable is reeled upon a drum I5. As the drum I6 is revolvedforwardly or backwardly, the cable I4 is reeled in or payed out and thetravelling block I 3 is caused to rise or fall within the derrick ll. Ofcourse, the drill pipe (not shown) is supported from the travellingblock l3 in the usual manner and carries a drilling bit upon its lowerend.

In drilling operations, the cable drum It is revolved by a suitableengine or motor (not shown) to reel in the cable l4, raising thetravelling block l3, and the drill pipe consequently being raised withinthe Well bore. The cable is payed out from the drum It simply throughthe action of the weight of the drill stem which pulls the travellingblock l3 downwardly and draws the cable M from the drum. A suitable bandbrake I! is provided upon one flange of the drum l6 for controlling itsmovement, and the rate and degree of paying-out of the cable therefrom.This invention, in part, controls the operation of the brake IT, therebystopping the paying-out of the cable M from the drum, or permittingunreeling of the cableat a rate which may be selected at will.

As shown in Fig. 2, a motive means such as an air motor 58, or any othersuitable type of motor or engine adapted to be driven by fluid underpressure or other readily-controllable source of power, is providedadjacent the drum l6 and drives an operating shaft [9 through a suitableselective speed changer 28. The speed changer 20 may be any suitable ordesirable type of device capable of varying the ratio between the speedsof rotation of the motor l8 and shaft l9,.and may be operated by asuitable gear shift or speed changer lever 2| for selecting variousratios of speeds. A telescoping splined coupling 22 is connected to theshaft i9 and couples a second operating shaft 23 to said shaft I9. Thisarrangement prevents rotation between the two shafts, but permitslongitudinal movement of the shaft 23 with respect to the shaft l9.

A worm gear 26 or other rotatable element is mounted upon the shaft 23and mesheswith a worm wheel 25 coupled to a suitable pulley 26. In turn,the pulley 2B is connected by a driving belt 21 to a pulley 28 mountedupon and rotating with the cable drum or reel IS; The worm wheel 25 isconnected to the pulley 25 through a suitable ratchet mechanism 28',whereby rotation of the pulley 2c in a clockwise direction, as viewed inFig. 2, is transmitted to the worm wheel 25, but rotation of the pulleyin the opposite or counter-clockwise direction is unimpeded, Otherrotatable elements and connections may be employed in this portion ofthe apparatus for accomplishing the same function. The describedcoupling has been found most desirable.

The shaft 23 is extended beyond the worm gear 24, being supported in asuitable bearing 29 and having its outer end 30 terminating adjacent anarm 3| or other actuating means secured to the brake-operating handle32. With this arrangement, longitudinal movement of the shaft 23 to theleft, as viewed in Fig. 2, causes the arm 3| to swing counter-clockwiseand tighten the brake band I1 upon the periphery of the cable reel 16.Such tightening of the brake band slows or stops the revolution of thecable reel according to the degree of force applied to the lever 3| bysaid shaft 23.

In the operation of this portion of the invention, assuming that it isdesired to take up or reel in cable onto the drum IS, the ordinarydriving machinery is employed for this purpose to revolve the drum in acounter-clockwise direction, as viewed in Fig. 2. When this occurs, thepulleys 28 and 26 are also driven in a counterclockwise direction, butthe ratchet mechanism 28' permits the worm wheel 25 to remain at rest orto revolve slowly. When it is desiredto pay out or unreel cable from thedrum, however, the latter is revolved in a clockwise direction,revolving the pulleys 28 and 25 in a clockwise direction and resultingin clockwise revolution of the worm wheel 25. Such revolution of theworm wheel causes the wormgear 24 to move to the left, forcing the end30 of the shaft 23 against the lever or arm 3|, tightening the brake I!and slowing or stopping the reel I6. In this condition of the apparatus,the motor l8 may be employed to regulate the speed of revolution of thedrum It, in that the motor may be driven at a desired speed, and bymeans of the speed changer 2d, the shafts Is and 23 will also be drivenat a selected or desired speed. This speed of revolution of the shaft 2%creates a selected speed of revolution of the worm wheel 25, andprovides for a certain speed of revolution of the pulleys 26 and 28along with the drum it. If the drum tends to revolve too slowly, theworm gear 24 will be revolved too rapidly by the motor E8 in relation tothe speed of revolution of the worm wheel 25, and will tend to move tothe right, as viewed in Fig. 2. Such movement shifts the shaft 23 to theright and releases the brake i 1, thereby allowing the drum iii toincrease its speed of revolution. Should the drum tend to overspeed andunreel cable too rapidly, the worm wheel 25 will be driven too rapidlyin the relationship to the speed of revolution of the worm gear 24, andthe worm gear along with the shaft 23 will be shifted to the left,tightening the brake band I? and slowing down the cable reel Hi. It isto be noted that the motor l8 does not drive or revolve the drum it, butmerely serves as a means for revolving the shaft 23 and the worm gear24, at a selected speed. The drum i6 is revolved by suitable engines ormotors, or by the weight of the drill stem carried by the cable M, andin turn, drives the pulleys 28 and 28 and the worm whee 25. According towhether the worm wheel 25 is being revolved too rapidly or too slowly,the worm 2d and shaft 23 will be shifted to the left or to the right toincrease or decrease the tension upon the brake band H and bring thespeed of revolution of the cable drum to the proper value. Of course,the longitudinal shifting of the shaft 23 is made possible by thesplined coupling 22 without requiring corresponding shifting of theshaft i9, and at the same time, the coupling effectively transmitsrotative motion between the two shafts.

It is obvious that the relative pitches of the worm 2d and the wormwheel 25 may be of any selected value, and, with proper design, willeliminate any possibility of the worm being driven by the worm wheel.Thus, no matter how great the load upon the cable l4 may be, the

a worm 2 may be driven with a small source of power and will control thefeeding out of cable from the drum without being susceptible to drivingby the drum. The maximum load placed upon the driving motor 38 does notexceed that necessary to overcome the friction of the system and topermit a braking force to be applied to the brake band IT. The actualbraking is done by rotation of the cable drum, and the need for heavy orcumbersome equipment is therefore eliminated. This point is emphasizedby the fact that rotation of the cable drum will apply the brake evenwhen no energy is being supplied to the driving motor. Actually, thebrake is applied by the cable drum and merely released by the motor.

Itv is not always possible or preferable to arrange the elementsprecisely as shown in Fig. 2, and it is sometimes not desirable to placethe worm and worm wheel mechanism upon the same side of the cable drumas the brake band 17. A modification is shown in Fig. 4, in which theshaft 23 carries at its outer end a hydraulic piston 33 enclosed withina hydraulic cylinder 35. A similar hydraulic piston 35, enclosed in ahydraulic cylinder 36, is adapted to have its piston rod 37 engage thearm 3| of the cable reel brake band handle 32. A suitable hydraulicfluid conductor 38 extends between the cylinders 34 and 36 so thatlongitudinal movement of the shaft 23 and piston 33 is reflected insimilar longitudinal movement of the piston 35 and the piston rod 31.The utilization of the hydraulic fluid conductor 39 permits the locationof the two cylinders at remote points, whereby the operating shaft 23need not be alined with the brake handle arm3l, as shown in Fig. 2.

As hereinbefore stated, any suitable source of motive fluid underpressure or other power supply may be employed for driving the motor 18,and any suitable means may be employed for regulating the supply ofpower to the motor so as to control the speed of operation thereof. Apreferred embodiment of the invention, however, includes a source ofcompressed air 39, as shown in Fig. 3, connected through a valve 46 to aheader or manifold ii. A second header or manifold 42 is connected tothe manifold 41 through a plurality of short conductors 43, eachconductor having therein an orifice valve 4 1. The apertures of thevalves 44 are of diifering values, and by opening different ones of saidvalves or different groups of said valves, fluid under pressure may besupplied at various rates to the header 42 from the header 4|. In thismanner, an initial control of the volume of mo tive fluid is provided.

A first conductor 45 is connected into the manifold 42 and extendsthrough a shut-off valve 46 to a supply pipe 41 leading to the motor [8.By opening the valve 46, driving fluid is supplied directly to the motor18 through the valve 44, and the speed of revolution of the motor !8will be controlled and regulated in accordance with the opening of oneor more of the orifice valves 44. For automatic control of the motor I8,a second conductor 48 leads from the manifold 42 to a hydraulicallyoperated valve 49. The valve includes a housing 59 having therein asliding valve 5| of the piston type, and having a hy-- draulie piston 52operatively connected to said valve. The conductor 43 is connected intoone side wall of the housing 56, and a similar conductor 53 extends fromthe opposite wall of the housing to the pipe 4?. Longitudinal shiftingof the valve 5! within the housing shuts oif, restricts, or regulatesthe flow of fluid from the conductor 48 to the conductor 53 in themanner customary in this type of valve. An adjustable spring 54 isprovided within the housing for applying a load to the valve structurein opposition to the force exerted upon the piston 52 by the hydraulicfluid.

For applying pressure to the piston 52, the load upon the dead end ofthe cable I4 is employed. As illustrated in Fig. 1, the dead end of thecable carries a clevis 55 which is pivotally connected to theintermediate portion of an arm 56 anchored to the derrick structure andadapted to swing in a vertical arc thereabove. The outer end of the arm56 bears upon the lower end of the piston rod 5'! of a piston 58confined within a hydraulic cylinder 59. A suitable conductor 6!:extends between the cylinder 59 and the housing 58, and a body ofhydraulic fluid or liquid 6! transmits force from the piston 58 to thepiston 52.

With this arrangement, and when the valve 46 is closed, the operation ofthe motor 18 may be regulated in accordance with the load exerted uponthe dead end portion of the cable l4, and it is possible to maintain aconstant drilling load upon a drill bit suspended from the travellingblock I3 by means of the drill stem. It is customary to support part ofthe weight of the drill stem from the travelling block, and to allowpart of said weight to bear against the drill bit to urge the same intothe formation being drilled. Obviously, as the drill is rotated andfeeds downwardly into the formation, cable must be payed out from thedrum IE to maintain the load upon the bit at a constant value. Thepresent inven" tion accomplishes this function by regulating the speedof rotation of the motor I8 in accordance with the load exerted upon thedead end of the cable M.

In the event the drum I6 is paying out cable too rapidly so as to applyan excessive portion of the weight of the drill stem as a load upon thedrill bit, the load upon the dead end of the cable it will be decreased,and the spring 54 will tend to move the valve 5i to the right, as viewedin Fig. 3, shifting the piston 52 to the right and moving the piston 58downwardly. As this occurs, the valve moves from the wide open position,shown in Fig. 3, to a partially closed position wherein the outlet fromthe conductor 48 is restricted, and the flow of motive or driving fluidto the motor through the conductors 53 and 41 is diminished. The motoris thus caused to revolve at a slower speed, and the overspeeding of thedrum It shifts the worm 2t and the operating rod 23 to the left againstthe brake arm 3! so that the brake band 57 is tightened and the drum IEis slowed down. Similarly, if the drum I5 is rotating too slowly, thedrill bit will dig faster than cable is payed out whereby the drillingload upon the bit will be reduced and the load upon the dead end of thecable 54 will be increased. This increasing of the load upon the cableswings the arm 55 upwardly, forcing the piston 58 upwardly and thepiston 52 toward the left and reduces the restriction of the corn ductor48 by thevalve 5!. The flow of motive fluid to the motor I 8 istherefore increased as the regulating valve 49 opens, whereby the motorwill be speeded up, resulting in releasing of the brake band H to apoint at which the drum l6 revolves at the proper speed and pays out thecable M at the proper rate.

It is obvious that the force exerted by the spring 54 may be adjusted bymeans of the screwthreaded follower 62 to compensate for the varyingweight of the drill stem as sections of pipe are added thereto orremoved therefrom, and that a substantially constant drilling load uponthe drill bit may be obtained in the manner described. At any time, thevalve 46 may be opened and the valves 44 regulated to provide anydesired speed of revolution of t e drum l6. Similarly, the revolution ofthe drum it may be reversed at any time so as to reel in cable or toassume the weight of any sudden load placed upon the travelling bloc i3.

A more detailed and specific embodiment of the invention is shown inFigs. 5 through 10 of the drawings. In Fig. 5, is illustrated thepreferred form of control mechanism for regulating the flow of motivefluid to the speed regulating motor. This control apparatus includes arectangular housing 63 adapted to be mounted upon a suitable support orstandard 64 and positioned at a convenient opera-ting height adjacentthe floor of the derrick or drilling rig structure. The housing includesa longitudinal horizontal partition 65 carrying a pair of posts 66 uponwhich a weight or scale beam 61 is mounted by means of a suitable knifeedge 08. The usual large and small weights 69 and I0, respectively, arelongitudinally slidable upon individual arms II and I2, respectively, ofthe scale beam 61, and indicating scales I are provided for designatingthe weight or load being exerted by the scale beam. An indicating fingeror tang I4 projects from the end of the scale beam and is confinedbetween a pin I5 carried upon upright supports 10, and a moveable keeperTI pivoted upon the supports i6. At the opposite end of the scale beam,the customary counterbalance weight I8 is provided, along with anadjustable balancing or zeroing weight "IS.

A second pair of posts 330 project downwardly from the partition 65adjacent its central portion, and an elongate weight lever BI has itsfulcrum or knife edge 82 bearing upwardly against the posts 80. The longarm or" the weight lever 81 is operatively connected to the scale beam61 by an adjustable link 83, and the short arm of the weight lever 85 isprovided with knife edges 84 bearing against the upper end of a yoke 85con nected to the upper end of a piston rod 86. The rod 06 extends intoa diaphragm housing 87 and is connected therein to a suitable flexiblediaphragm 83.

The weight and beam structure which has been described takes the placeof the adjustable spring 54, previously described, and provides a meansfor placing a selected and exact load acting downwardly upon thediaphragm 88. For opposing this load, a suitable hydraulic fluidconductor 89 is connected into the lower portion of the housing El andplaces the housing into communication with a source of hydraulic fluidto be described hereinafter, and which exists under a pressureproportional to the load upon the dead end of the cable I4. With thisarrangement, as the pressure exerted by the hydraulic fluid upon theunder side of the diaphragm 38 is less than or is greater than the loadexerted by means of the piston rod 88, the weight lever 0| will becaused to swing clockwise and counter-clockwise, and may be employed forcontrolling the rate of flow of iiuid to the previously-described fluidmotor.

A control valve 9%, is mounted in one end of the housing 63 beneath thepartition 65, substantially in vertical alinement with the adjustablelink 83. The valve includes a cylindrical housing 9i having therein acylindrical liner 92 provided with valve ports 93 and 04. A piston typevalve core 95 has a sliding fit within the liner 92, and has its upperend secured to a flanged cap 95 which fits loosely over the open upperend of the housing St. A substantially L-shaped arm 97 is pivoted to thelong arm of the weight lever 8i, and is constantly urged toward saidlever by a suitable spring 92. A set or stop screw 99 limits theswinging of the arm 9'! and provides for radial adjustment of thespring. The arm is connected to the valve core 95 by means of a flexiblewire I00 of sufficient strength as not to stretch when a tension isapplied thereto, but which is sufficiently flexible as to bend undercompression when the arm 9? is swung downwardly. Since the outer end ofthe lever 8i swings in an are rather than in a straight line, and sincethe valve 95 must move rectilinearly, the flexible wire I00 is employedto eliminate the need for guides and. pivoted joints in the connectionbetween the weight lever and the valve core.

Motive fluid under pressure is supplied to the device through a pipe I0!connected through a plug valve I02 to a pipe T I03. One branch of 8. theT I03 is connected into the valve port 93, and a suitable conductor I04leads from the other valve port 94 to a pipe T I05. A bypass pipe I06 isprovided with a shut-off valve I01 and extends between the Ts I03 andI05 for bypassing the valve 90, when such is desired. A header I03,equivalent to the header 4l, is connected into the T I05, and isprovided with a plurality of branch conductors i09 carrying drilledorifices H0 and shut-off valves III. The lower ends of the conductorsI09 are connected into a header IIZ, equivalent to the header 42, and aconductor I I3 leads from the latter header or manifold to the fluidmotor I8.

As stated hereinbefore, the pressure exerted upon the under side or" thediaphragm 88 will vary from time to time whereby the weight arm 8| willbe allowed to swing clockwise or counterclockwise. When the pressureexerted on the underside of the diaphragm is low, as occurs when toomuch weight is being applied to the drilling bit, the lever 3i swingsclockwise which raises the valves core 95, shutting off or restrictingthe port 94. When this occurs, the flow of fluid through the valve tothe headers and the supply pipe H3 is restricted or reduced, with theresult that the revolution of the cable drum I6 is slowed down, and aportion of the weight or load is removed from the drilling bit.Conversely, if the bit is underloaded and the pressure upon thediaphragm 8i) is high, the lever 81 swings counterclockwise, exposingthe port 93 an additional amount and permitting a greater flow of fluidand faster revolution of the cable drum. For convenience in operation,the valves I07 and Iii are provided with suitable operating handles orlevers H4, and a pressure gauge I I5 is connected into the conductor 89for indicating the pressure being exerted therein. In accordance withthe previous description of the invention, the orifice plates lit are ofvarious and different sizes, and opening or one or more of the valvesIII results in varying rates of flow of the motive fluid to the motorit. When desired, the valve I0! may be opened to bypass the controlvalve t0 and permit the revolving of the cable drum It at any desired orselected speed.

A preferred embodiment of the cable anchor is shown in Figs. 6, 10, 11and 12. The anchor includes a base plate or support lit, adapted to beanchored suitably adjacent the derrick floor or the ground surface, andhaving a pair of upstanding side plates I ii. The plates I i? aregenerally triangular in shape and having extensions lie of reducedcross-section extending outwardly of the base plate 5 it. A plate i i9is connected between the extension lit and joins the two together. Apair of cheek plates I23 are pivoted adjacent one vertical edge or" theplates II! upon a transverse shaft H9 and have their free endsprojecting beneath the extensions Iiii. Between the plates I2 l arelatively narrow flanged reel I2I is rotatably mounted and receives anumber of turns of the dead end pcrtion of the cable It. A clamp I22secures the projecting portion of the cable to the cheek plates, andprovides an anchor for said cable.

In order to permit rotation of the reel I2! when such is desired, but tohold the reel immovable with respect to the cheek plates at other times,the reel carries a plurality of transverse openings I23 adapted to bealined with openings I2 5 in the cheek plates and to receive a cotter orlooking pin I25 passed through the openings I24. Enlarged openings i261in the side plates III facilitate insertion and removal of the pin. Whenthe pin I25 is in place, the reel and cheek plates move together as aunit, but because of their small amplitude of movement, there is noengagement between the pin and the walls of the opening I25.

A hydraulic cylinder I28 is disposed vertically between the extensionsII8 adjacent the plate I I9 and is adjustably secured thereto by boltsI29 engaging in slotted openings I35 formed in lateral ribs I3Iprojecting from said extensions. A hydraulic piston I32 is carriedwithin the cylinder I28 and has a piston rod I32 projecting downwardlyinto engagement with a plate I20 carried upon the upper edges of thecheek plates In use, the dead end of the cable I4 is receivedtangentially by the reel 2I and is passed therearound several times, theprojecting end of the cable being secured in the clamp I22. Any upwardstress or load upon the cable I4 thus tends to swing the reel and thecheek plates upwardly, as viewed in Fig. 6, and to swing the plate I20upwardly, forcing the piston I32 upwardly within the cylinder I28. Inthis manner, the load placed upon the cable is reflected as the pressureexerted by the piston I32 upon the hydraulic fluid within the cylinderI28, this pressure being communicated through the conductor 35, which isconnected into the upper end of the cylinder, to the underside of thediaphragm 38 in the weight control structure shown in Fig. 5.

It is to be noted that the distance between the shaft II9, which is thecenter about which the cheek plates I20 are pivoted upon the side platesH1, and the center of the cable I4 is much less than the distancebetween the shaft and the point of engagement on the piston rod I32.With thi arrangement, a considerable mechanical advantage is had, andboth the dimensions of the cylinder I28 and the pressures within thecylinder are kept within reasonable limits. At the same time, thecylinder may be adjusted toward or away from the shaft M9 by means ofthe bolts I29 and slotted openings I38, and compensation made for theuse of cables of various diameters. Since the effective lever armbetween the shaft H9 and the cable I4 is viewed as extending from thecenter of the shaft to the axial center of said cable, provision isdesirably made for adjusting the anchor mechanism in accordance with thediameter of cable in use. With this structure described, as cables ofvarious sizes are employed, the cylinder I 23 may be shifted toward oraway from the shaft I I9 to make proper compensation for the differencein cable diameter.

A preferred embodiment of the worm wheel and worm gear structure isshown in Fig. 7, including a speed changing device I33, having a driveshaft I 34 to which is connected the fluid motor IB (not shown in thisfigure). A splined operating shaft I35 extends from the speed changerI33 into a gear housing I35 within which the worm wheel I31 and the wormgear I33 are mounted. The worm gear I351! is secured upon the splinedshaft I 35, which is movable longitudinally with respect to the speedchanger. The gear, therefore, may not revolve on the shaft, but theentire gear and shaft structure may shift longitudinally. A toothedratchet wheel I 39 is disposed centrally of the worm wheel I31, and isprovided with ratchets I45 having leaf or drag springs I4I thereon. Anoperating shaft I42 projects from the worm gear I38 and extends into alateral housing I43 projecting from the housing I36. A hydraulic pistonI44 is provided within the housing I43 upon the outer end of the shaftI42, an enlarged View of this structure being shown in Fig. 9 of thedrawings. In the latter view, the piston I44 is shown as being hollowand substantially cylindrical, and as being connected to the shaft I42by a suitable thrust bearing I 45. A cap I46 forms the outer end of thehousing I43 and encloses the outer end of the piston I44. As shown, boththe housing and the cap are flanged at their point of joining and adomed diaphragm member I41 has its outer marginal edge or periphery I48clamped. and secured between the abutting faces of the cap and thehousing. The central portion of the diaphragm is secured upon the faceof the piston I44 by a plate I 49 and bolts I50. As shown, the clearancebetween the piston and the housing and cap is sufficient to permitdoubling of the diaphragm structure, whereby an effective sealing isobtained without the employment of piston rings or similar structureswhich are subject to leakage. The diaphragm structure may roll uponitself as the piston moves from the position shown in Fig. 9 to theposition shown in Fig. 7, and a complete seal is maintained at alltimes. The hydraulic fluid conductor 38 (shown in Fig. 4) is connectedinto the outer end of the cap I45 and leads to the cylinder 36 and thepiston 35 for operating the brake band I1.

It is often desirable to disconnect thi entire control mechanism fromthe cable drum I5, and a structure for this purpose is shown in Fig. 8of the drawings. In this modification, the worm gear I33 and the wormwheel I31 are mounted within the housing I36 in the manner illustratedin Fig. 7, and an operating shaft I 5| projects through the side wallsof the housing. The worm wheel I3! is rotatably mounted upon the shaftI5I by means of bearings I52, the shaft, in turn, being journalled inthe walls of the housing upon bearings I53. Suitable oil seals I54 areprovided to prevent oil leakage through the side walls of the housingaround the shaft. A spline clutch I55 is keyed upon the shaft I5I and isadapted to engage a splined collar I56 formed integrally with theratchet wheel I39. In the position of the elements shown in Fig. 8, theclutch is disengaged and the shaft I5I may turn independently of theratchet wheel I39 and of the worm wheel I3l. Upon shifting to the left,however, the clutch I55 engages the splined collar I56 and locks theelements against rotation with respect to one another.

A hydraulic or air pressure operated means is provided for shifting theclutch to and from its operating position, and includes a double-actingpiston I51 engaging within a pair of opposed cylinders I58 carried uponthe top wall of the housing I 36. A link I59 connects the piston to anarm I60 which revolves a shaft I6I extending down one face of thehousing I35 and carrying a suitable gear wheel I62 at its lower end. Thegear wheel I62 meshes with a gear rack I63 which is reciprocally mountedwithin the wall of the housing I36 and the inner end of which hasengagement with the clutch I 55. Transverse shifting of the piston I54in accordance with the admission of fluid under pressure to one of thecylinders I58 causes swinging of the arm I63, rotation of the shaft 55!,and reciprocal movement of the gear rack I 52. In this manner, theclutch I55 is moved into and out of engagement with the splined collarI56 so as to place the control de- 1 l vice in operative or inoperativeconnection with the cable drum Hi.

In the use of the peferred embodiment of the invention herein described,the cable drum may be run at any desired speed, or it may be set byadjustment of the weights 59 and "it to place any desired load on thedrill bit and to maintain such loading at a constant value.

The advantages and benefits flowing from the invention herein disclosedare manifold and involve many important factors in safety and ease ofoperation. As pointed out hereinbefore, the operating and controlmechanism is subjected only to light loads of a frictional nature, and.hence the elements of the system may be made quite small and relativelyinexpensive. This permite the various elements of' the device to befabricated with high safety factors without involving expensive andheavy parts, thereby considerably reducing the probability of mechanicalfailure within the device. Nevertheless, should some mechanical failureoccur, so as to stop the motor it or interrupt the flow of motive fluidunder pressure flowing thereto, the motor will simply stop, therebyapplying the brake and terminating the feed-oil or payout of cable fromthe reel It. In some existing devices using direct electrical control,hydraulic control, or electrically actuated brakes, a power failure willpermit the paying-out of cable and so increase the load upon the drillbit so quickly that the drill pipe is twisted off before the operatorcan seize control of the drilling mechanism. In the present invention,the customary cable reel brake is employed for control of the cable drumor reel, and since the brake is already present and is designed tohandle in an adequate fashion the loads and forces involved, the presentinvention does not require the provision of additional braking orcontrol devices of sufiicient massiveness and strength as to be capableof handling the heavy loads involved.

A further very important feature of the invention lies in the fact thatthe operator can instantly take over control of the drilling machine. Itis only necessary to operate the brake lever by hand to take over thecontrol, and there is no necessity of manipulating clutches, switches,valves, and the like to disengage the automatic control before takingover manual control. Indeed, if hoisting is required, the hoisting rigclutch may be engaged at once without stopping or altering the operationof the control device since the brake will be instantly released as soonas the cable drum begins to rotate to take in cable.

Under emergency conditions, a few seconds delay in operation ormanipulation of the drilling machinery may cause heavy damage, and nodelay is encountered through use of the present invention.

It is further to be noted that so long as the automatic control deviceis in operation, there will be established a maximum rate of cablepayout. Thus, should the drill bit .or the drill stem suddenly breakthrough into a void in the forma tion, dropping of the bit and the drillstring will be prevented since the brake will instantly take hold andprevent such dropping. This is very important, especially in deepdrilling where many tons of drill pipe are involved. Such large massneed only be dropped a small distance to do enormous damage. Thiscontrol of maximum rate of feed-out is also important in reamingoperations. In such cases, the entire load of the drill stem must besuspended from the drilling machinery, and the present device providesadequate control and regulation of such an operation.

Fhebwpass valves 45 and I9? are of great value when controlled rapidshifting from upward to downward movement of the drill stem and fromdownward to upward movement thereof, are required, such a in fishingoperations. The hoisting mechanism cannot get out of control when thepresent device is being employed, and very rapid shifting is facilitatedby the ease of engagement and disengagement of the control mechanismwith the drilling machine.

As pointed out hereinbefore, the adjustable mounting of the hydrauliccylinder I28 provides for compensation of the control device in accordance with the size cable being employed. This adjustableness of thecylinder also is of importance permitting exact calibration of thestructure to permit direct reading from the scale 53 of the actual loadupon the travelling block l3. In practice, the scale 13 is removable,and a plurality of such scales are provided in accordance with thenumber of lengths of cable from which the travelling block is suspended.After the proper scale has been attached, the empty travelling blockhook may be balanced to zero upon the scale and then a known weightlifted by said hook. If the scale fails to balance at the setting ofthat known weight on the beam, the cylinder on the deadline anchor isshifted and adjusted by trial until the reading on the scale whenbalanced corresponds with the known weight. Accurate calibration ofthe'clevice and adjustment thereof to a proper reading is therebypermitted and facilitated.

The foregoing description of the invention is explanatory thereof andvarious changes in the size, shape and materials, as well as in thedetails of the illustrated construction may be made, within the scope ofthe appended claims, with out departing from the spirit of theinvention.

What I claim and desire to secure by Letters Patent is:

1. Control apparatus for cable drums including, driving means, anelement driven by said driving means, a second element adapted to bedriven by the cable drum, a connection between the first and secondelements, a support for the first element, the latter element beingmovable longitudinally of the support with respect to the secondelement, brake means for the cable drum, and a force-transmittmgconnection between the brake means and the first element whereby forcefor tightening the brake means is supplied by the cable drum through theconnection between the first and second elements and through theforcetransmitting connection to the brake means.

2. Control apparatus for cable drums inoluding, driving means, alongitudinall shiftable worm gear driven by the driving means, a secondgear adapted to be driven by the cable drum meshing with the worm gear,brake means for the cable drum, and a force-transmitting connectionbetween the brake means and the worm gear whereby force for tighteningthe brake means is supplied by the cable drum through the worm gear andthe second gear and through the force-transmitting connection to thebrake means.

3. Control apparatus for cable drums including, driving'means, anelement driven by said driving means, a second element adapted to bedriven b the cable drum, an operating connection between the elements,the first element being shiftable with respect to the second element,

brake means for the cable drum, and'a movement-transmitting connectionbetween the brake means and the first element for transmitting movementof the first element to the brake means, whereby movement and force totighten the brake means is supplied from the cable drum through theconnection between the first and second elements and through themovement-transmitting connection to the brake means.

4:. A control apparatus for cable drums including, driving means, anelement revolved by said driving means, a second element adapted to berevolved by the cable drum, 2, driving connection between the elements,a support for the first element permitting shifting of the latter withrespect to the second element, brake means for the cable drum, and amovement-transmitting connection between the brake means and the firstelement for transmitting movement of the first element to the brakemeans, whereby movement and force to tighten the brake means is suppliedfrom the cable drum through the connection between the first and secondelements and through the movement-transmitting connection to the brakemeans.

5. Control apparatus as set forth in claim 4, and means for regulatingthe driving means.

5. Control apparatus as set forth in claim 4, and a splined connectionbetween the driving means and the first element.

7. Control apparatus for drilling equipment having a hoisting cablecarried by a cable drum and an anchor for the dead end of the cable,including, a driving motor adapted to be driven by fluid under pressure,a pressure fiuid conductor leading to the motor, a metering valve insaid conductor, operating means for the valve connected to the anchor, acoupling between the motor and the cable drum, brake means for the cabledrum, and actuating means for the brake means connected to saidcoupling.

8. Control apparatus for drilling equipment having a hoisting cablecarried by a cable drum an anchor for the dead end of the cable,including, a driving motor adapted to be driven by fluid under pressure,a pressure fluid conductor leading to the motor, a metering valve insaid conductor, operating means for the valve conneoted to the anchor, acoupling between the motor and the cable drum, brake means for the cabledrum, and hydraulic actuating means for the brake means connected tosaid coupling.

9. Control apparatus as set forth in claim 7, wherein the couplingbetween the motor and the cable drum includes, an element revolved bythe motor, a second element revolved by the cable a drivin connectionbetween the elements, and a support for the first element permittingshifting of the latter with respect to the second element, the actuatingmeans for the brake means being operated by the shifting of said firstelement.

19. Control apparatus as set forth in claim 7, wherein the couplingbetween the motor and the cable drum includes, alongitudinally-shiftable operating shaft driven by the motor andoperating the brake actuating means, a worm gear on the shaft, and aworm wheel meshing with the worm gear adapted to be driven by the cabledrum.

11. Control apparatus as set forth in claim 10, wherein. the couplingbetween the motor and the cable drum includes, a first shaft driven bythe motor, a second longitudinally-shiftable shaft splined to the firstshaft and operating the brake actuating means, a worm gear on the secondshaft, and a worm wheel meshing with the worm gear adapted to be drivenby the cable drum.

12. Control apparatus as set forth in claim 7, wherein the couplingbetween the motor and the cable drum includes, a speed changer driven bythe motor, a first shaft driven by the speed changer, a worm gear,splines connecting the worm gear with the first shaft, a worm wheelmeshing with the worm gear, a ratchet for connecting the worm wheel withthe cable drum, and means connected with the worm gear for operating thebrake actuating means.

13. Control apparatus as set forth in claim '7, wherein the anchor forthe dead end of the cable includes, a support, a reel structurepivotally mounted on the support, means on the reel for securing thedead end of the cable thereto, a hydraulic cylinder carried by thesupport, and a piston in the cylinder having a piston rod, said rodbeing adapted to be actuated by the reel, and said cylinder beingadjustable on the support toward and away from the pivotal center of thereel, the piston and cylinder comprising the op erating means for themetering valve.

14. Control apparatus as set forth in claim 7, wherein the anchor forthe dead end of the cable includes, a support, a reel structurereceiving the cable tangentially, means on the reel for securing thecable thereto, said reel being eccentrically mounted for revolution uponthe support about a center closely adjacent the point of tangency of thecable to said reel, the reel and support forming the two main elementsof the anchor, a hydraulic cylinder carried by one of said mainelements, and a piston in the cylinder having a piston rod engaging theother of said main elements, the point of engagement of the piston rodbeing relatively remote from the center of revolution of the reel, thepiston and cylinder con prising the operating means for the meteringvalve.

15. Control apparatus as set forth in claim '7, wherein the anchor forthe dead end of the cable includes, a support, a reel structurepivotally mounted on the support, means on the reel for securing thedead end of the cable thereto, the reel and the support forming the twomain elements of the anchor, a hydraulic cylinder carried by one of saidmain elements, and pressureexerting means in. the cylinder having anoperating stem engaging the other of said main elements, said operatingstem being adjustable toward and away from the pivotal center of thereel, the pressure exerting means and the cylinder comprising theoperating means for the metering Valve.

16. Control apparatus as set forth in claim 7, wherein the anchor forthe dead end of the cable includes, a fixed support, a movable supportpivotally mounted upon the fixed support, a reel pivotally mounted uponthe movable support, said reel receiving the cable tangentially, meansfor securing the reel against rotation with respect to the movablesupport, means on the movable support for securing the dead end of thecable, and pressure-indicating means associated with the movable and thefixed supports.

17. Control apparatus as set forth in claim 16, wherein the reelsecuring means includes a pin engageable with the movable support, thereel having a plurality of transverse openings adapted to receive saidpin in a plurality of positions of the reel with respect to the movablesupport.

18. A control apparatus for cable drums ini5 cluding, driving means, anelement revolved by said driving means, a second element adapted to berevolved by the cable drum, a' driving connection between the elements,a support for the first element permitting shifting of the latter withrespect to the second element, brake means for the cable drum, actuatingmeans for the brake means connected to the first element and operated byshifting thereof, and a ratchet connection between the cable drum andthe second element.

19. A control apparatus for cable drums including, driving means, anelement revolved by said driving means, a second element adapted to berevolved by the cable drum, a driving connection between the elements, asupport for the first element permitting shifting of the latter withrespect to the second element, brake means for the cable drum, actuatingmeans for the brake means connected to the first. element and operatedby shifting thereof, and control means for regulating the driving meansincluding, a source of fiuid under pressure for operating the drivingmeans, a pressure fluid conductor between said source and the drivingmeans, and adjustable valve means in said conductor.

20. A control apparatus for cable drums including, driving means, anelement revolved by said driving means, a second element adapted to berevolved by the cable drum, a driving connection between the elements, asupport for the first element permitting shifting of the latter withrespect to the second element, brake means for the cable drum, actuatingmeans for the brake means connected to the first element and operated byshifting thereof, and control means for regulating the driving meansincluding, a source of fluid under pressure for operating the drivingmeans, a pressure fluid conductor between said source and the drivingmeans, and a metering valve in said conductor.

21. Control apparatus for cable drums including, driving means operableat a selected speed, brake means for the cable drum arranged to beapplied and released to maintain the speed of revolution of the drum ata predetermined ratio with respect to the speed of operation of thedriving means, a motion-transmitting connection between the drivingmeans and the cable drum, said connection including an element having anormal position occupied when the cable drum and the driving means areoperating at the predetermined ratio, said element being mounted forshifting from its normal position when the relative speeds of operationof the cable drum and the driving means vary from said predeterminedratio, an actuating connection between said element and the brake forapplying and releasing the brake means in accordance with the shiftingof the element, and means for controlling the speed of operation of thedriving means.

22. Control apparatus for cable drums including, brake means for thecable drum, driving means operable at a selected speed, a motiontransm'tting connection between the driving means and the cable drum andhaving an element arranged to shift position when the speed of operationof the cable drum varies from a predetermined ratio with respect to thespeed of operation of the driving means, the brake means being appliedand released by the position shifting of said element, and means forcontrolling the speed of operation of the driving means.

23. A control apparatus as set forth in claim 22, a weight-responsivemeans responsive to the load sustained by the cable drum, and anoperating connection between said weight-responsive means and thespeed-controlling means for the driving means for maintaining apredetermined load on the cable drum.

JOHN C. SLONNEGER.

References Cited in the file of this patent UNITED STATES PATENTS NumberName Date 1,779,480 Loomis Oct. 28, 1930 1,779,656 Brauer Oct. 28, 19301,954,176 Johnson Apr. 10, 1934 FOREIGN PATENTS Number Country Date305,939 Great Britain Feb. 11, 1929 647,491 Germany July 6, 1937

